Rotary engine



July 20, 1937- J. 1. KEMPTHORNE ROTARY ENGINE Filed March 3, 1934 2 Sheets-Sheet 1 INVENTOR James A Kemp 2% vrwe ly 20, 1937- J. L. KEMPTHORNE ROTARY ENGINE Filed March 3, 1934 2 Sheets-Sheet? lNVENTOR ment rotary pumps.

Patented July 20, 1937 UNITED STATES PATENT} OFFICE 8 Claims.

This invention relates to improvements in pumps, engines, compressors and the like and more particularly to means for and methods of controlling the pressure of positive displace- It is an improvement on the devices shown in my prior Patents No. 1,904,374, patented April 18, 1933, and. No, 1,930,480, patented October 17, 1933.

I have heretofore shown a rotary type positive 10 displacement pump construction in which a spherical segment operated as a rotor in the hemispherical or spherical casing and made possible the intake, compression and exhaust of fluid mediums. In my present invention I have improved the mechanism so that I can continuously control the pressure output rendering the pump discharge of substantially constant pressure which is necessary in certain industrial fields. I have also improved the operating characteristics by an improved abutment which has angular faces to cooperate with the rotor so that improved porting and sealing can be obtained.

One of the principal objects of my invention is to provide a variable capacity, constant pressure pump of the rotary, positive displacement type in which the pressure may be initially set at a predetermined value by any desired manual or automatic means and the discharged fluid will be under substantially constant uniform pressure regardless of capacity demand within the range of the pump.

Another object of my invention is to provide a rotary type positive displacement pump which is particularly adapted for pumping fuels and lubricants irrespective of their viscosity, so that a more exact control of the fuel or lubricant can be had and so that constant pressures with capacity variations 'to supply demand can be had withoutthe usual reliefivalves and other regulating devices. I l

Another object of my invention is to provide a rotary positive displacement pump with a cons'tant pressure control device operable from its own :or other pressuresources to automatically 45 vary the capacity in accordance with the fluctuations in the, pressure source and'to act, for example, as an unloading device so that the-motor can come up to speed-beforethe pumpstarts to work.

' A.i'urther and-more detailedobject of the in- 55 ment plate with faces in angular relation and with a smaller port volume so that the pump has a higher volumetric efficiency and a better vacuum lift.

Another object of my invention is to provide a simple and highly effective control for reversing the flow of a pump of the rotary, positive displacement type, such control being either manual or mechanical, and which may be remotely controlled.

Further objects and advantages of my invention will appear from the following description thereof taken in connection with the attached drawings which illustrate preferred forms of embodiment to which my invention is susceptible and in which:

Figure 1 is a vertical section substantially through the center of an improved type rotary pump having a constant pressure control;

Figure 2 is an exploded perspective view of cer-' tain of the respective operating parts of the pump shown in Figure 1;

Figure 3 is a substantially central vertical section of a modified form of control showing the use of a sylphon bellows diaphragm controlling-- the pressure by regulating the rotor position;

Figure 4 is a partial vertical section of a further modified form of construction using a tensionin'g device for controlling the position of the pump rotor;

Figure 5 is a partial central vertical section of a still further modified form of construction havoil filled type of retarder for the control arm movement. I

A simplified form of positivedispla'cement r0- tary pump as more particularly shown in Figure 1, comprises a two-partcasing I'll andl I, the part II having a flange Ila adapted to besecured to a supporting framework. The ported part ofthe 1 casing l'l carries the driveshaft-l! to the, end of which is secured the rotary abutment plate. ll.

The shaft I2 is journaled in suitablebearingstli and is preferably provided withfsuitable; fibrous siredrnanner.

w The rotary ,abutment plate-l4; is "shown in packing l6 for, oiling purposes. The packing is -secured in. positionbya suitable, collar Hand an adjustmentbushing- "a or in anyotherdegreater detail at-the right invFigure :2;anda-is' 3' 1 shown to have a plurality of faces a, which, if

continued to a central point, would be angularly disposed with respect to each other. The center of the plate however, is provided with a pai-tially cylindrical groove I 4b, to receive the cylindrical retaining member lab hereinafter described. The faces a are also cut away in the center as shown at Mo to cooperate with the ports in the casing part II. g

The casing I part Illcarries a hemispherical housing I! which is held'against the casing part II. If desired these parts could be made integral. The hemispherical housing l3 receives the. hemispherical rotor l8 which is substantially filled by it. The rotor is preferably provided with suitable sealing rings Illa and as the rotor is a full hemisphere, these may be cylindrical in shape.

The rotor I8 is shown in greater detail in the center of Figure 2 and is shown to have a transverse sealing member l 817 which is held to the flat face of the rotor by suitable screws l8c. When the parts are assembled the rotor is driven by the abutment plate and as the rotor is held in fixed position with respect to the abutment plate ll, all reaction on the housing l9 due to pressure on the face of the rotor, is relieved. This materially reduces friction in operation. Due to the shape of the groove llb in the rotary plate and the substantially cylindrical bar l8b the rotor may oscillate however and the porting of the face of the rotor'will contact first with one angular face of the rotary abutment plate and then with the other face. This action is brought about by ofi-setting the rotor axis with respect to the axis of the abutment plates as hereinafter described. The abutment plate i4 and the rotor l8 will be moved longitudinally until the rotor engages the hemispherical wall in the chamber l9 due to the action oi. springs lib on the collar He which en-' and the more the pump is operated, the better.

the flt will be. If desired the rotor wall may be relieved throughout a substantial-part of its area to reduce wear on the respective parts.

The'housing l9 carries a controlarm 25 which controls the position of the rotor with respect to the relative angularity between a normal to the rotor face or the axis on which it rotates and the axis of the drive shaft and abutment plate M. This angle directly controls the capacity of the pump for the compression chamber 3| between the faces of the abutment chamber l4 and the rotor member I6 is governed by it.

The rotor position control arm 25 is provided with suitable slots 25a which closely fit similar grooves in the hemispherical casing l3 so that there is a relatively low degree of friction and a. relatively low loss of pressure. The positioncontrol arm 25 extends through a slot l9a' in the hemispherical casing and on its inner'end is pro.- vided with a central bore25b to receive a detachable spindle member 26 which is keyed to the transverse bar |8b by the pin 28, the spindle 26 .passingthrough a slot 21 in the rotor f8. 'It will thus be seen that movement of the rotor position control arm 25 will effectively manipulate the angularity of the rotor.

The intake to the pressure chamber is through the port 30 and due'to the angularity of the rotor to the axis of the drive shaft l2, one portion of the rotor will first contact with one of the faces a. of the abutment plate I 4 to leave a space 3| between the other face Na and the other portion of the rotor for the reception of fluid which enters said space from point 30 through the channel Me of the abutment plate. Upon' rotation of the shaft, the sides of the abutment plate close the port 30, and the fluid within the space 3| is compressed between the rotor l8 and abutment plate I2 and discharged through channel I40 and the discharge conduit 32. Thence it passes through the conduits 33 into the intermediate pressure control chamber 34 and to the final pressure outlet 35.

The intermediate pressure control chamber 34 is preferably in the end of the cylinder 20 having the piston 2| which is held in upper position against fluid pressure by the spring 22. The piston divides the chamber and forms a gas tight portion below the piston. The piston is carried on the 'piston rod 24 which extends through suitable adjustable bushings to connect with the rotor position control arm 26 as by a screw joint shown at 21. A relief valve 36 'may extend through cylinder wall 20 into chamber 20a to relieve the chamber from any collection of liquid therein.

The automatic operation of the device is therefore as follows: The discharged fluids under pressure nonnally hold the piston in a position against the operation of the spring 22 thus maintaining the angular relation between the rotor and the drive shaft. If the pressure should tend toincrease, however, the piston 2| would be forced downwardly to reduce the angularity and therefore reduce the capacity of the rotary pump. If the pressure should decrease as would take place .with an increase of capacity demand in the pres- 1 sure discharge line 35, the piston 2| would move upwardly thus increasing the angularity of the rotor and therefore increasing its capacity.

The movement of the piston may be further restricted by a certain .compression below the piston 2|.

piston, the gasket expands and acts as a seal against the gases in the lower part of the chamber as well. Adjustments may be made to initially set the tension of the spring by means of the adjustable collar 23 and the member 23a which cooperates with the spring. The control may be set for a determined pressure and the pressure aperture opening into chamber 20a. and rely.on

the spring 22 to balance the pressures in chamber 34. No dash pot action would then be had.

A pump of this type is especially suitable for pumping viscous liquids as it will act to pump regular amounts of liquid irrespective of var ations in viscosity. -It is also suitable for fuel pumps as the pressure being constant, the capacity will be proportional to the speed and no floats, relief valves or other control means will be necessary. In automotive work this will permit the elimination of the carburetor and fuel pump and the substitution of a simple mixing valve or valves. It is also possible .in such cir cumstances to manually control the capacityby use of levers of any desired type which may be synchronized with other valve controls or ignb tion controls.

In the following forms of embodiment of my One or more gaskets 2 ia'may be used,' although, due to the pressure on the top of the invention, I have shown slightly modified forms of rotor position control to change the position of the rotor as hereinbefore described. As the casing, rotor and rotor drive are the same or may be of any other desired construction, all the details of constuction are omitted in the following flgures for the sake of clarity.

The constant pressure control shown in Figure 3, includes a chamber 40 preferably of cylindrical form, having a compression chamber 4| adapted to receive the fluid discharge from the pump (not shown) or from any other source of fluid through the conduit 42, and discharging in turn, out of the main discharge conduit 43. The position control shaft is indicated at 44 and it contacts with the inside of a bellows diaphragm 45 mounted within the control chamber 40. A spring 46 is also preferably enclosed in the diaphragm 45 in order to hold the control arm 44 in a tensioned and relatively fixed position, free from any unnecessary fluctuation. The bellows diaphragm is sealed in the bottom of the casing 40 thereby making a gas tight chamber.

The initial tension of the spring 46 may be changed by varying the position of the chamber 40 with respect to the pump casing 41. An adjustment member 48 is adapted to move the chamber 40 away from or toward the pump casing 41 and this will tend to lengthen or shorten the eflective length of the control shaft 44 and therefore control the relative pressure of the pump.

Pressure increases within the chamber 4| will tend to force the top of the bellows 45 downward to change and reduce the operating angle be;- tween the rotor and the abutment plate. This will control the pressure discharge due to the reduction in pump capacity. Reduction of pressure however will cause the diaphragm to move upwardly and the capacity will thus increase. The normal pressure will thus correspond to the fixed spring tension. There is no possibility of leaks'with the bellows 45, and the control may thus be used where absolute sealing of the fluids under pressure is essential.

Another modified form of construction is shown in Figure 4 in which the rotor control arm 58 holds the rotor (not shown) in position under spring tension by the spring 5|. A housing 53 surrounds the spring to permit free movement and the spring may be adjusted to any desired amount as by the adjustment 52. Although a coil spring is shown, it is clear that other tensioning devices could be used with substantially equivalent results.

In this construction of a single spring controlling the relative angularity of the rotor, any variations in pressure discharge will cause a movement of the control arm 50 to vary the capacity. This pressure change Will be oil'set by the spring 5|, however and the pressure delivered will be substantially constant irrespective of line fluctuations as the tension of the spring is entirely independent of any change of pressure.

A slightly modified form of uniform pressure control is shown in Figure 5. The control housing 60 is provided with a spring 64 which is carried on the spring seat 640. The spring seat 64a is conveniently supported by bolts 64b extending to the top of the control housing 60. Other supporting means for the spring could be substituted if desired.

A spring head 69 is mounted on the upper end of the extension rod 61 which is connected to the piston rod 68 and thence to the rotor position control arm 66. The piston rod 68 carries a piston 65 which acts as a dashpot against the pressure in the pump casing 660..

The operation of this form of embodiment depends on an increased pressure in excess of the tension of the spring which will act on the rotor (not shown) to move the spring 64 and dash pot. If due toan increased volume demand, the pressure should drop, the spring would change the rotor position to increase the capacity and keep the pressure constant. Any sudden movement however due to a change in pressure which would normally cause a sudden movement of the rotor position control arm 66 is damped by the dash pot piston 65 and the rotor moved through the proper angle in a relatively slow manner. The arrangement of connections is such that it is impossible to suddenly vary the capacity of the pump although ,a continuous pressure differential will efiect the movement of the control arm 65.' This form of construction is therefore particularly desirable for certain industrial units as close control can be obtained.

A reversible form of control is shown in Figure 6. The rotor position control arm I0 is held in any fixed position by means of an adjusting member II which may have a spin gear Ha thereon for rotation. The adjusting member H may preferably be in the form of a screw operating in look nut 13, or it may be any other form of take up means. The adjusting member is connected to the control arm 10 by link 14 and a suitable swivel 15. The spin gear may be mechanically moved by the motor 16 and gear 11 connected in any desired manner and adjustment of the rotor arm may be facilitated. The pressure may thus be varied from a remote point in accordance with the capacity required so that the pressure will remain constant. The rotor position may also be changed beyond a center point so that the pressure is reversed, or a vacuum set up, or it may be held at the center point until the desired shaft speed has been obtained and thereafter moved to obtain the requisite pressure.

An oil controlled pressure device for a rotor of the hereinbefore described type which is simple in construction and highly effective is shown in Figure '7. This form of the device includes a modified form of rotor casing 80 which has an integrally formed hemispherical chamber to receive the rotor 8| which is driven from and cooperates with the abutment plate 82. The casing 80 has an extension housing 80a to which is secured the pressure control mechanism chamber 83. A spring 84 is mounted in this chamber and it abutsa piston 85 which in turn is carried by piston rod 86. The piston rod 86 is secured in any desired manner to the rotor position control arm 81. p

The piston 85 flts loosely in-the chamber 83 and is preferably provided with a series of holes 85a. around its head. It also may have a gasket 85b. The chamber 83 is preferably filled with oil or other liquid and the casing extension 80a is similarly filled. The gasket 851) thus forces the oil to pass through the small holes or ports 85a in the piston and. retards the operation of the piston. Changes of pressure, however will be reflected in the movementof the control arm of the rotor and the movement of the piston 85 against spring tensionwhich may be adjusted by any desired means. As the piston movement controls the angularity of the rotor with respect to the axis of rotation of the abutment plate, the capacity of the pump is readily varied by adjustments of the spring 84. The spring may be set at any desired corresponding pressure and this pressure will be maintained by the pump.

The rotor and casing and control are preferably carried in the same housing and no leakage of oil is possible. Increase in pressure will hold the oil in place and the normal leakage past the rotor may be used for filling the chamber 83 or it may be filled through the filling plug 88. r

I have therefore provided means for automatically controlling the rotor position of a positive displacement. rotary pump. This controls the capacity of the pumpwhich however, is proportional to the pressure so that by suitable adjustments, the pressure of the pump may be set at any desired amount and it-will remain substantially constant with the speed of the pump as all variations will be reflected to the rotor position control arm and the capacity varied to automatically control the pressure. Variable characteristics may be obtained by various arrangements of springs, compression chambers, diaphragms and dash-pot constructions so that various industrial uses can be satisfied.

While I have shown preferred forms of embodiment of my device, I am aware that modifications may be made thereto and I therefore desire a broad interpretation of my invention within the scope and spirit of my disclosure herein and of the claims appended hereinafter. 1

I claim: a

1. A positive displacement rotary engine of the class described comprising a ported casing having a hemispherical chamber therein, a hemispherical rotor mounted in said casing, an abutment having flat faces angularly displaced with respect to each other cooperating with said rotor, means to simultaneously drive said abutment and rotor, the axis of rotation of said rotor when in nor-- mal operative position being at an angle to the axis of rotation of the abutment whereby'the rotor comes into substantial contact with al-' ternate faces of the abutment, movable means connected with the rotor and extending at an angle to the rotor axis whereby movement ,oL

the rotor axis causes linearmovement of said movable means, yieldable means of predetermined strength normally holding said movable means in predetermined position but responsive to changing fluid pressure loads acting upon the cooperating faces of saidengine to allow movement of said movable means and thereby of said rotor axis, said fluid pressure loads acting on the cooperating faces of said engine constituting the sole means for causing said movement of said rotor axis, and means acting on said movable means to'prevent sudden movement thereof and thereby to prevent fluttering of the'r'otor.

2. A pump, compressor, or like mechanism comprising a casing having a hemispherical chamber therein, a hemispherical rotor mounted in the chamber, and an abutment having flat faces angularly disposedwith respect to each other, said abutment closing the chamber, and having a driving shaft thereon, said faces converging toward the center whereby a diametrically disposed contact is established between the rotor and the abutment,means to rotate the rotor and lock the rotor to the abutment, including a slot in said abutment more than half round in cross section, and

a cooperating cylindrical shaped projection on said rotor and means to vary the angular position of the rotor in the chamber with respect to the axis of said abutment, said means including a spindle member projecting into said rotor, 8.

a hemispherical chamber therein, intake and exhaust ports in said casing, a hemispherical rotor mounted in said casing, an abutment cooperating secure and seal said rotor and abutment together intermediate of said faces.

4. A pump, compressor, or like mechanismcomprising a casing having a chamber therein, an abutment member closing the chamber, a rotor member occupying a spherical portion of the chamber, said abutment member being cut away to provide faces converging toward the center, means connecting said members diametrically at the center but permitting the angle between the axes of said members to be varied, means connected with one of said members for rotating both simultaneously, intake and exhaust ports on opposite sides of the casing and a channel in each face of said abutment member extending substantially radially across the same and opening into the side thereof and adapted to register alternately with said intake and exhaust ports, whereby upon rotation of said abutment member, communication is established between the chamber and the ports when the channels register with the ports and is cut off when the channels are not in registry therewith.

5. A positive displacement rotary engine of the class described comprising a casing having a hemispherical chamber therein, a pair of 00- operating rotatable. members mounted in said casing including a hemispherical rotor, an abutment having angular flat faces cooperating with said rotor and connected thereto, means to simultaneously rotate said abutment and rotor, the

axis of rotation of said rotor normally being at an angle to the axis of rotation of the abutment whereby the rotor comes into substantial contact with alternate faces of the abutment, a constant tension means connected with one of said rotatable members and controlling the angular relation between the rotor axis and the abutment axis whereby fluctuations of pressure will cause a variation in the capacity of the engine, said constant tension means including a piston member and a piston arm extended at an angle to the axis of said rotor, means to control the movement of said piston member in proportion to the direct pressure discharge of the engine, and means to maintain said rotor close to the wall of the spherical chamber and take up for wear including strong spring means mounted in recesses in said casing and bearing against said abutment axially thereof whereby to force chamber therein, intake and discharge ports the abutment so that said rotor axis may assume K positions on either side of said abutment axis, or a position in line therewith, and yieldable means of predetermined strength normally maintaining said angular relation varying means in a position such that the rotor axis lies in a plane at one side of said abutment axis whereby fluid is dis charged by the mechanism out of said discharge port, but responsive to changing fluid pressure loads within said chamber acting on the opposing faces of the rotor and abutment members to permit movement'of said rotor axis to positions abutment member cooperating with said partially spherical member to close said chamber, said partially spherical member and said abutment member having opposing working faces, the axes of said abutment member and of said partially spherical member normally having an angular relation to each other, means to rotate the abutment member and partially spherical member whereby to draw fluid into said intake port and to discharge the same through said discharge port, and means connected with one of said members to support said one member in varied positions of axial angular adjustment with respect to the other of said members, said angular relation supporting means including a constant pressure means movable in response to changing fluid pressure loads on said working faces of aforesaid members whereby the delivered pressure of said pump remains substantially constant, said, fluid pressureloads on said working faces constituting the sole means for causing the i angular relation of saidaxes to-be varied, andrelation varying means to prevent the sudden operation of said angular relation varying means and thereby to prevent flutteringv of the position of the variable member,

8. A positive displacement rotary type device of the class described, comprising a casing having a hemispherical chamber therein, intake and discharge ports in said casing, a hemispherical rotor mounted in said casing for rotation and linear movement therein, an abutment cooperating, with said rotor, said abutment having divergent faces angularly disposed with respect to each other, means to rotate said abutment and rotor simultaneously, yieldable means of predetermined strength connected with said rotor and adapted normally to maintain the same in a predetermined linear position, so that its axis lies at an angle to the axis of the abutment and so that, upon: rotation, the rotor comes substantially into contact with alternate faces of the abutment, said yieldable means including a rod connected with said rotor atan angle to the axis of the rotor, a piston on said rod, a housing surrounding said piston and a portion of said rod, spring meansin said housing and cooperating with said piston and rod normally to maintain I changing fluid pressure loads acting on the said surfaces of the rotor and the abutment constituting the sole means for causing said linear, movement of said rotor, and fluid pressure damping means in said housing cooperating with said piston to prevent sudden movements of the same and said rod.

\ JAMES L. KEMPTHORNE. 

